Reversible heat pumps



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Feb. 5, 1963 R. c. SCHLICHTIG 3,076,321

' REVERSIBLE HEAT PUMPS Filed July 15, 1960 7 Sheets-Sheet s AND CONTENT MOTOR 64 IN VEN TOR.

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REVERSIBLE HEAT pumps Filed July 15, 1960 7 Sheets-Sheet 5 OOOOOOOOOO EESEE VO/IZ 1/4 PEFRIEERATING' COMPRES$0R FJIGS IN VEN TOR. flzp'csmz/m r/a A Trek/v15) Feb. 5, 1963 R. c. SCHLICHTIG 3,076,321

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INVENTOR. RALPH C. SO/Z/(HT/G BY A T TOR/WE) United States PatentO-fiice 3,076,321 REVERSIBLE HEAT PUMPS Ralph C. Schlichtig, 11212 3rd 8., Seattle 88, Wash. Filed July 15, 1960, Ser. No. 43,245 6 Claims. (Cl. 62-270) This invention relates to a new and improved heat pump incorporating a heat exchanger in which the heat pump utilizes gas as the main thermodynamic substance and in which power is supplied to the heat pump by a motor driven blower and/ or by change of vapor pressure.

The subject application is a continuation in part application of application Serial No. 829,905, now abandoned, entitledRe versible Heat Engines, filed July 27, 1959, by .Ralph C. Schlichtig, the applicant in the subject application.

Heat pumps using air as a working substance have been built, but they have the usual disadvantage of being very bulky. Their eificiency is usually so low that excessive power is required for transferring desired quantities of heat from the lowtemperature source to the higher temperature place of utilization. Such prior art heat pumps usually have the additional problem of lubrication because of sliding parts.

Attempts have been made to build heat pumps with large air handling capacity through employment of rotors with fixed vanes and in which pressure recovery has been attempeted by means of a plurality of equalizer tubes interconnecting successive high pressure intervane compartments with successive low pressure intervane compartments. However, an equalizer tube will not recover in excess of fifty percent of the pressure energy if there are no leakage or friction losses. In practice, an increase in the number of these prior art equalizer tubes requires a multiplication of time for rotation of the rotor by the number of equalizer tubes used. This results in a pro- ,portional increase in volume leakage, so that leakage becomes a predominate loss. There is also a proportional increase in bulkiness. In accordance with one of the teachings of this invention the provision of a single pres- ,sure inverter tube eliminates this difficulty.

Therefore, an object of'this invention is to provide in a gas type heat pump, operating with small differences in the temperature of the gas, means for handling large volumes of gas with a minimum of leakage and friction losses, to thereby obtain .a maximum of useful heat exchange.

Another object of this invention is to provide in a heat pump means for providing an interchange between mechanical power and a change in vapor content of gas.

A further object of this invention is to provide in a heat pump means for obtaining cooled liquid by. the evaporation of a liquid inthe presence of a precooled gas.

Still another object is to recover power from the condensation of vapor from wet air and using the recovered power in a heat pump to heat dry air for dehydrating purposes.

A further object of this invention'is to provide in a heat pump for preheating gas flowing over cooling coils, "such as the cooling coils of a conventional heat pump, so as to prevent frost from forming on the fins of the cooling coils of the conventional heat pump.

Still another object of this invention is to condition humid air by removing water vapor therefrom.

A still further object of this invention is to provide refrigerated air Without dehydrating the air or without the utilization of a defrosting mechanism.

Other objects of this invention will become apparent when taken in conjunction with the accompanying drawings in which: 1

FIG. 1 is a schematic diagram of a heat pump embody- Patented Feb. 5,1963

ing teachings of this invention and in which means is provided for cooling gas below the temperature. of the coldest available water supply, for air conditioning purposes;

FIG. 2 is an isometric view of the heat pumpshown in FIG. 1; a

FIG. 3 is a cross section viewo'f the heat pumps h'o'wn in FIG. 2 taken along the lines 3-3; I FIG. 4 is a schematic diagramof a heat pump embodying still further teachings of this invention and in which means is provided for obtaining'cooled water; FIG. 5 is a schematic diagram of a heat pump embody ing still other teachings of this invention and in which means is provided for obtaining dry heated-air; I

FIG. 6 is a schematic diagram of a non-frostingqheat pump embodying other teachings of-this invention and in which means is provided for preheating .gasflowing over the cooling coils of a conventional auxiliary heat pump, so as to prevent frost from forming on the;fins of the cooling coils of the auxiliary heat pump;

FIGS. 7A and 7B are enlarged views of .the wventuri pressure inverter interconnecting membershown in FIGS. 1 and 3 through 6 in which the flow of gas. through the member and the manner in which back flow .is prevented .are illustrated;

pressure inverter member side, and associated components which are similar to those-of FIGS. 1 through 3, as well as the cycle of pressure inversion.

Referring to FIGS. 1 through 3 there is shown a heat pump 10 in which means is provided for obtaining an interchange between mechanical power and a change in vapor content of gas by the evaporation of a liquid, specifically water 11, in the presence of enclosed gas at moderate temperature, to thereby provide ,cooled'gas for airconditioning purposes.

In general, the heat pump 10 comprises a rotor housing 12 having consecutively a closed first sector portion 114 which is the closed portion ,of the housing 12 shown at the right in FIG. 1, an open second sector portion '16 which is the open portion of the housing 12 shown at the bottom in FIG. 1, a closed third sector portion 18 which is the closed portion of the housing 12 at the left in FIG.

"1 and which is oppositely disposed from thefirst closed sector portion 14, and an open fourth sector portion 20 which is the open portion of the housing 12 shown at the topin FIG. 1. The rotor housing 12 is disposed around a rotor 22 having a hub 24 and a plurality of equally spaced vanes 26, which are fixed to the .hub 24 and extended radially out therefrom so that there are at all times at least two of the vanes 26 in each oftlie four sec tor portions 14, 16, 18 and '20. Thus, the sector portions '14, 16, 18 and 20 combined represent the volume swept out by one of the, vanes 26 upon one revolution of the rotor 22. In practice, the rotor 22 and the associated parts are so constructed as to have a minimumoftransfei' of heat between the rotor 22and the associated gas. The housing 12 is so disposed around the rotor 22 as to be in close proximity to allof the peripheral edges of the vanes 26 as they come into the first and third sector portions 14 and 18, respectively, of the rotor housing 12, to thus successively establish isolated incomingintervane cornpartments 28, 29 and 30 and outgoing intervane compartments 34, 35 and 36. By close proximity to all of. the

In order to discharge the changed gas contained within the outgonig intervane compartments 34, 35 and 36 to ambient space and in order to obtain a new charge of gas from the ambient space, an ambient manifold 38 is connected to the fourth sector portion 20 of the rotor housing 12. In particular, the ambient manifold 38 comprises a scroll case 40 or discharge portion for deflecting the changed gas from the outgoing intervane compartments 34, 35 and 36, and a pair of intake ducts 42 for receiving a new charge of gas from the ambient space and directing it into the intervane compartments 43, 44 and 45 of the rotor 22.

For the purpose of precooling the ambient gas received from the ambient space before it passes into the intervane compartments 43, 44 and 45, a precooler 46 is disposed at the receiving end of each of the intake ducts 42. As shown, the precooler 4-6 comprises a coil 47 for receiving coolant and radiating fins 48 attached to the coil 47 for absorbing and transferring heat. However, it is to be understood that other types of precooling devices (not shown) could be substituted for the precooler 46 of FIG. 1.

A sealed heat exchanger enclosure 50 is suitably connected to the second sector portion 16 of the rotor housing 12 in order to provide a pressure isolated enclosure for receiving the gas from the incoming intervane compartments 28, 29 and 30. For the purpose of providing evaporating surfaces 51 for the water 11 received from a spray device 52 which directs the water 11 onto the sur faces 51, a heat exchanger 54 is disposed within and suitably secured to the enclosure 59. In practice, the heat exchanger 54 may be constructed from inert material such as stone. On the other hand, in order to deflect the gas received from the incoming intervane compartments 28, 29 and 39 onto the evaporating surfaces 51, a deflecting scroll case 56 is suitably secured to the rotor housing 12 and positioned as shown. A sump and trap 57 is so connected to the enclosure 50 that it receives surplus liquid from within the enclosure t) without permitting gas to escape or enter the enclosure 50.

As illustrated, a reversible blower 58 is suitably secured to the enclosure 50 by means of an air duct 60 having a passageway 62 which is in communication with the interior of the enclosure 50. However, it is to be understood that other suitable conventional blowers (not shown) could be substituted for the blower 58. As shown, a butterfly valve 63- is disposed within the passageway 62 and functions to control the fiow of air or gas through the passageway 62. An electric motor 64 is mechanically connected to the blower 58, as shown, to drive the blower 58 and thus transmit power to the enclosure 59. A motor 66 shown in FIG. 2 in operation drives the rotor 22.

In order to enable adiabatic expansion of the gas disposed within the outgoing intervane compartments 34, 35 and 36, a port 68 is disposed in the third sector portion 18 of the rotor housing 12. In order to simultaneously enable adiabatic compression of the gas disposed within the incoming intervane compartments 28, 29 and 30, port 70 is provided in the oppositely disposed first sector portion of the rotor housing 12.

In accordance with this invention, an interconnecting pressure inverter member 72, constructed in the form of a unidirectional venturi is interconnected between the ports 68 and 70. As illustrated, the eccentric intake section 74, of the member 72, converges eccentrically with respect to the port 68 into a central section 79. In practice, the intake section 74, of the member 72, is suitably sealed to the rotor housing 12 so as to prevent the leakage of gas from the outgoing intervane compartments 34, 35 and 36 to ambient space.

The outgoing divergent discharge section 86, of the member 72, is highly streamlined and is suitably sealed to the rotor housing 12 so as to permit the recovery of kinetic energy of the gas flowing through the interconnecting member 72 as pressure energy, to thus eflfect adiabatic compression of gas within the incoming intervane compartments 28, 29 and 30.

More than one pressure inverter member, such as the member 72, may be used in parallel if they interconnect identical intervane compartments and function simultaneously as a single pressure inverter member.

Port cover tabs or closing members 82 are suitably secured to the ends of each of the vanes 26 in order to cover and effectively seal the ports 68 and 7t) and prevent direct passage of gas between adjacent incoming intervane compartments and between adjacent outgoing intervane compartments during the time that oppositely disposed vanes 26 separating the adjacent intervane compartments are passing over the ports 68 and 70.

The cycle of operation of the heat pump 10 will now be described. Air from ambient space passes over the precooler 46 where its density is increased by cooling. This air of increased density then passes through both of the intake ducts 42 and enters the intervane compartments 43, 44 and 45 through an opening 88, thus replacing the air already present in the intervane compartments 43, 44 and 45. The replaced air is removed from the intervane compartments 4-3, 44 and 45 by virtue of the increasing radius of the deflecting scroll case 40 which compels the air to follow its expanding contour. Upon clockwise rotation of the rotor 22 by means of the motor 66, the air of increased density is carried by the rotor 22 until it is discharged into the sealed heat exchanger enclosure 50 by the action of the deflecting scroll case 56. The deflected gas of increased density then impinges upon the evaporating surfaces 51 of the heat exchanger 54 where it is further cooled by evaporation of water. The evaporator surfaces 51 are kept supplied with moisture by means of the spray device 52. Excess water is allowed to escape through the sump and trap 57. Simultaneously pressure is maintained in enclosure 50 by the action of the blower 58 with the valve 63 in the open position. The gas of increased pressure then flows through the intake openings 90 into the intervane compartments 92, 94 and 96, to thus replace in equal volume the gas of increased density that had been previously discharged onto the evaporating surfaces 51.

Upon further rotation of the rotor 22 in the clockwise direction, the gas of increased pressure-volume product disposed within the intervane compartments 92, 94 and 95, is carried upwards until said gas Within the intervane compartment 92 comes into the space corresponding to the outgoing intervane compartment 35 and in communication with the port 68, at which time a portion of this gas enters the port 68 and is accelerated as it enters the central section 79. Thus the pressure energy of gas leaving the port 63 is converted into kinetic energy in the central section 79, of the interconnecting member 72. As the gas passing through the central section 79 enters the diverging outgoing discharge section (as shown in FIG. 7A), the kinetic energy is again converted into pressure energy to raise the pressure of air in the incoming intervane compartment 29. Therefore, the gas within the outgoing intervane compartment 35 undergoes adiabatic expansion to produce adiabatic compression of the gas in the incoming intervane compartment 29. In practice, the pressure inverter member 72 is designed large enough so that the adiabatic inversion of pressure between gas in the outgoing intervane compartment 35 and gas in the incoming intervane compartment 29 will take place within the time that the incoming intervane compartment 29 is in communication with the port 70. During the first half of this pressure-inversion cycle the pressure of the gas in the outgoing intervane compartment 35 is greater than the gas disposed within the incoming intervane compartment 29. The pressure difference causes the kinetic energy of the gas flowing in the central section 79 to increase. Thus, at the middle of the pressure-inversion cycle the pressure of the gas disposed within the incoming intervane compartment 29 becomes substantially equal to the pressure of the gas disposed within the outgoing intervane compart- HA; I

-central section 79 have decreased to zero.

ment-35. Then during the second half of the pressureinversion cycle the kinetic energy within the central section 79 of the pressure inverter member 72 causes gas to continue to flow from the outgoing intervane compartment 3-5 to the incoming intervane compartment 29 even though .the pressure of the gas disposed within the outgoing intervane compartment 35 becomes lower than the pressure of .the gas disposed within the incoming intervane compartment 29 due to overshooting. After the completion of the pressure-inversion cycle, the flow of any substantial gas in the reverse direction through the pressure inverter member 72 toward the port 68 is prevented by the cyclonic effect in the eccentric intake 74 of the pressure inverter member 72. This blocking action can be seen from FIG. 7B. If it is assumed that a small amount of gas after the completion of the pressure-inversion cycle does go back- .wards in the direction from right to left, as shown, then gas in the eccentric intake section 74 rotates cyclonically as shown in FIG. 7B. As gas moves from the periphery of the rotating mass into the center to enter the port 68, conservation of angular momentum demands a rotation at increased speed as in the case of cyclones. The high angular speed of rotation sets up a centrifugal reaction which prevents gas from flowing into the center and out through the port 68.

FIGS. 9A and 913, relative to apparatus similar to that shown in FIGS. 1 through 3, further illustrate the cycle of pressure inversion hereinbefore described when the interconnecting member 72 is in communication with one pair of intervane compartments. As can be seen from FIGS. 9A and 9B the outgoing intervane compartment is bounded by the hub 24, the rotor housing 12 and vanes 26A and 26B which carry closing members 82A and 82B, respectively, while the incoming intervane compartment is bounded by the hub 24, the rotor housing 12 and vanes 26C and 26D which carry closing members 82C, and 82D,

respectively. It is to be noted that since FIGS. 9A and 9B illustrate the apparatus when viewed from the interconnecting member side, the direction of rotation of the hub 24 and associated vanes 26A, 26B, 26C and 26D is opposite to that shown in FIG. 1 in which the apparatus is viewed from the side opposite the interconnecting member 72.

Referring to FIG. 9A, the first half of the pressure inversion cycle begins as closing members 82A and 82C uncover ports 68 and 7 respectively, thus placing the outgoing intervane compartment defined by vanes 26A and 2613 in communication with the incoming intervane compartment defined by vanes 26C and 26D by way of the interconnecting member 72. The close spacing of circular dots in at the outgoing intervane compartment end .of the interconnecting member 72 illustrates that the air is more compressed here than at the incoming intervane compartment end where the circular dots m are farther spaced. Each circular dot m represents a unit mass of air. As the air pressure as illustrated is greater at port 68 than at port 70, there is a force acting on each mass m of air in the interconnecting member 72. These forces are shown as acting on each mass m of air by respective arrows directed toward the circular dots. The air masses .m are thus accelerated in the direction of the forces until a maximum velocity is reached at the middle of the pressure-inversion cycle. The time of a half-cycle is short so that onlya limited amount of air leaves the interconnect- -ing,member 72 at port 70. But any mass before so leaving the interconnecting member 72 must transfer its kinetic energy to the remaining air in the central section 79 of the interconnecting member 72 by being decelerated by the divergence of the outgoing divergent discharge section 80. This is the well known venturi action. By the middle of the pressure inversion cycle the air pressure of the interconnected intervane compartments has reached equilibrium and the forces on the air masses within the But by this time the masses m in the central section 79 of the interconnecting member results in compressing the air in the incoming intervane compartment defined by vanes 26C and 261) while the air pressure is reduced in the outgoing intervane compartment defined by vanes 26A and 26B until all the stored energy of the air mass in the interconnecting member 72is expended at the close of the cycle. At the close of the cycle the ports 68 and 70 are closed by the closing members 82B and 82D, respectively. p

The gas which was increased in density by the precooler 46 is thus further increased in density and in pressure by action of the pressure inverter member 72 and this gasof further increased density within the incoming intervane compartment 29 is carried down, upon further rotation of the rotor 22, and discharged into the sealed heat exchanger enclosure 56. The pressure-volume product of the gas within the sealed heat exchanger enclosure 50 is thus conserved. I

Gas moving upward in intervane compartment 35 is further cooled by adiabatic expansion. It is cold when discharged through manifold 40 and, can be used for refrigeration purposes.

'As the gas of further increased density is carried down and discharged into the sealed heat exchanger enclosure 50, and gas of increased pressure is carried by the rotor 22 until it comes into communication with the port-68, the above described action is repeated.

In practice, the heat pump 10 is so constructed and the rotor 22 is driven at such a speed that the hereinbefore described pressure-inversion cycle can be completed in .the tirneof passage of one intervane compartment, of the rotor 22, from one positiorrto the adjacent position.

Referring to FIG. 4 there is illustrated another embodiment of the teachings of this invention in which water is chilled below wet bulb temperature. Like components of FIGS. 1 and 4 have been given the same reference characters. The main distinction between the apparatus of FIGS. 1 and 4 is that in the apparatus of FIG. 4 the pressure inverter member 72 is reversed in position so that the eccentric intake section 74, of the pressure inverter member 72, is in communication with the port 70 and the divergent outgoing section is in communication with the port 68. Also the pressure in heat exchanger en'- closure 50 is less than ambient pressure. The electric motor 64, in the embodiment shown in FIG. 4, drives the blower 58 in the direction to function as an evacuating pump. Water 99 from the spray device 52 is at as low a temperature. as a convenient sump (not shown) will provide. The gas disposed within the sealed heat exchanger enclosure 50 is reduced to a pressure below atmospheric pressure to speed evaporation.

Specifically, in operation air from ambient space passes into both of the intake ducts 42 and into the intervane compartments 43, 44 and 45, through the opening 8-8, to replace the vapor laden gas previously disposed Within the intervane compartments 43, 44 and 45. The displaced vapor laden gas is discharged to ambient space by the action of the radially deflecting scroll case 40. The dry ambient air disposed within the intervane compartments 43, 44 and 45, upon rotation of the rotor 22 in a clockwise direction is carried downward until the dry air within the intervane compartment 45 comes into the position of the incoming intervane compartment 29 and into communication with the port 70. Air then flows into the central portion 79 where it flows with high velocity (preferably subsonic). As it flows on into the diverging outgoing section 80, this kinetic energy of velocity is converted into pressure energy which brings the pressure of the gas in the outgoing intervane compartment 35 to a pressure value above the pressure of the air in the incoming intervane compartment 29 in a manner similar to that described with reference to the heat pump 10 of FIG. 1. This means air moving downward, by the action of the rotor 22, is preexpanded and cooled before reaching the position of the intervane compartments 92, 9'4 and 96. Here due to the diverging scroll case 56, the preexpanded cooled air is removed from the intervane compartments 2, 94 and 96 and is deflected into the sealed heat exchanger enclosure 50 and over the evaporator surfaces 51 Where rapid evaporation takes place.

The useful purpose obtained by evaporation is that heat is absorbed in the process which 6001s the water 99 which is flowing over the evaporating surfaces 51. In order to accomplish this useful purpose, the blower 55% must operate as a vacuum pump to remove the excess volume produced by evaporation of the Water 99. The cooled water is removed by means of the sump and trap 57.

Upon further rotation of the rotor 22, in a clockwise direction, the cool moist air from within the sealed heat exchanger enclosure t} enters the intervane compartments 92, 94 and 96, through the openings h), to replace the expanded ambient air previously discharged into the sealed heat exchanger enclosure 5i}. The vapor laden gas of reduced pressure within the intervane compartments 92, W. and 96 is then carried upward, as shown, until it comes into communication with the port 62 at which time the vapor laden gas of reduced pressure is adiabatically compressed, thus increasing the temperature of the gas within the intervane compartments 92, 94 and 96 that have now successively come into the position of the outgoing intervane compartment 35. This gas of increased temperature upon further rotation of the rotor 22, in a clockwise direction, is then discharged through the deflecting scroll case 4th to ambient space.

Referring to FIG. 5 there is illustrated still another embodiment of this invention in which wet air is dehumidified and heated, to thus provide dry heated air at the output of the scroll case 40. The main distinction between the apparatus of FIGS. 4 and 5 is that in the apparatus of FIG. 5 cooling coils 192 of an auxiliary heat pump 104 replace the heat exchanger 54 and the spray device 52, of FIG. 4. In particular, the auxiliary heat pump 104- includes a refrigerating compressor 1% which functions to maintain a low pressure in the cooling coils 162 by promoting rapid evaporation of refrigerant liquid Hi8 disposed within refrigerator cooling coil 102. As refrigerant vapor is compressed by the refrigerator compressor 1%, it is forced to flow to a condenser 110 where the vapor is converted back to liquid with the evolution of heat which is carried away by air circulated by means of a fan 112. The condensed liquid 1&8 is stored in a reservoir 114 until it is allowed to recirculate by passing a thermal-expansion regulator valve 116. However, it is to be understood that the cooling coils 162 are representative of any conventional heat pump.

In operation with the butterfly valve 63 open and the electric motor 64 deenergized, vapor laden air passes into the intervane compartments 43, 44- and 45 through intake ducts 42 to replace outgoing dehydrated air previously disposed within the intervane compartments 43, 44 and 45. Upon rotation of the rotor 22 in the clockwise direction the vapor laden air within the intervane compartment 43, 44 and 45 is successively adiabatically expanded as it comes into communication with the port 70 and a portion of this vapor laden air flows through the pressure inverter member 72 to successively produce adiabatic compression of the outgoing dry air disposed Within the outgoing intervane compartments 34, 35 and 36 as hereinbefore explained.

The adiabatically expanded vapor laden air is carried by the rotor 22 and i discharged into the sealed heat exchanger enclosure 50, where it is deflected over the cold cooling coils 102, to thus condense water vapor from the vapor laden air. The condensed liquid is drained off through the sump and trap 57. The reduction in pressure-volume product maintains a reduced pressure within the sealed heat exchanger enclosure 5%. Vacuum in the enclosure 59 is regulated by the flow of ambient air into the sealed heat exchanger enclosure 59 through the reversible blower 58.

The dry air within the sealed heat exchanger enclosure 50 is then carried by the rotor 22 until it comes into communication with the port 68 where adiabatic compression takes place. This adiabatic compression raises the temperature of the dry air which reduces its relative humidity. The air of reduced relative humidity, upon further rotation of the rotor 22 by the motor 66, is discharged to ambient space through the deflecting scroll case 40 Where it may be used for drying purposes. The drying racks or other drying equipment are not shown.

With the butterfly valve 63 still in the open position and with the blower 58 driven by the electric motor 64 so as to function as an evacuating pump, the cycle of operation is the same as previously described for the apparatus of FIG. 5 except that a further reduction of pressure of the gas within the sealed heat exchanger enclosure 5% is effected. Therefore, greater adiabatic compression ratio is effected for the outgoing dry air within the outgoing intervane compartment 35 which produces a higher degree of heating of the air discharged out through the deflecting scroll case 46.

With the butterfly valve 63 closed, in operation the cycle of operation of the apparatus of FIG. 5 is substantially the same as previously described with reference to this apparatus. However, the dehydrated air discharged from the deflecting scroll case do will be at a tempera ture that is intermediate of the temperature of the air obtained in the two previously described conditions of operation of the apparatus of FIG. 5.

FIG. 6 illustrates a heat pump 118 which functions to deliver heat from the radiator fins 129, of the condenser 110, without the formation of frost on the cooling coils Th2 disposed within the sealed heat exchanger enclosure so, and in which like components of FIGS. 5 and 6 have been given the same reference characters. The main distinction between the apparatus of FIGS. 5 and 6 is that in the apparatus of HG. 6 the pressure inverter tube 72 is reversed in position from that shown in FIG. 5 and the blower 58 in operation functions as a pressure pump to increase pressure of the air within the sealed heat exchanger enclosure 5% to thus elevate the temperature of the air within the sealed heat exchanger enclosure 50 to a value well above the dew point.

In operation, outdoor ambient air is drawn in through the intake ducts 42 into the intervane compartments 43, 4-4 and 45, thus replacing the refrigerated air previously disposed Within the intervane compartments 43, 44 and 45. Upon rotation of the rotor 22 in the clockwise direction, the ambient air within the intervane compartments 43, 44 and 45 is drawn down until the ambient air within the intervane compartments is successively brought into communication with the port '76 where adiabatic compression takes place as hereinbefore described. The adiabatic compression raises the temperature of this incoming air well above the dew point. Upon further rotation of the rotor 22 the air of increased temperature is discharged into the sealed heat exchanger enclosure 50 where it impinges on the cooling coils 102 where heat is given up to the cooling coils 102. This heat transfer can take place without the formation of moisture on the cooling coils 182 (in the form of frost) since the temperature of the air within the sealed heat exchanger enclosure 50 remains above the dew point.

The resulting chilled air within the sealed heat exchanger enclosure 50 is then carried by the rotor 22 until it comes into communication with the port 68 where the chilled air is adiabatically expanded. This further lowers the temperature of the outgoing air to a value which may even be well below the dew point. Test runs have shown this discharged chilled air to appear as a quite visible fog as it is discharged out the deflecting scroll case 40 upon further rotation of the rotor 22 in the clockwise direction.

FIG. 8 illustrates test data taken from a heat pump operating in accordance with the general features of this invention using a modestly streamlined, ten-inch-long by one and one-quarter-inch diameter, pressure inverter venturi tube (curve A), as compared with operation that could theoretically have been possible with a cross passage tube that would achieve perfect pressure equalization (curve B). Curve C shows the cubic feet of gas that would be lost per minute due to unrecovered compression in the rotor of the same device illustrated by curve A if therewere no pressure inverter venturi tube connected between outgoing and incoming intervane compartments. Pressure tests were taken on a sealed heat exchanger enclosure 50 Whenused with a ten vane rotor having a displacement of 1.35. cubic feet per revolution. The pres sure in the sealed heat exchanger enclosure 50 was maintained at 55 centimeters of water on the measuring manometer, by means of the blower 58 acting as an evacuating pump It is seen by the dip in the curve A that the pres sure inverter tube 72 functions to the best advantage at a given speed range. In practice, a pressure equalizing tube (not shown) would show volume loss approaching curve C at higher rotor. speeds, instead of following the straight ideal curve. B. Thus, the practical necessity of the pressure inverter tube 72 becomes apparent.

The above mentioned tests were taken on a heat pump similar to the heat pump 100 of FIG. 4 except that no water was applied by thespray device 52. Thus, the test data illustrates losses obtained when there is no volurnechange due to evaporation or condensation. The curves B and C were computed on the same basis.

The most favorable speed ,of rotation of the rotor 22 is inversey proportional to the number of vanes 26 provided the ratio of the volume of gas within the pressure inverter tube 72 as compared to the volume of gas within the intervane compartments, such as the compartment 29, remains constant. This ratio was five percent in the case of the test data shown by curve A. If a greater pressure in the sealed heat exchanger enclosure 50 is used, the volume ratio should be increased in proportion. If the most favorable design speed is to be changed, the diameter of the pressure inverter tube 72 should be changed in proportion. The apparatus embodyingthe teachings of this invention has several advantages. For instance, volumetric and friction losses are maintained at a very low value. This is extreme'y important in such heat pumps operating at small temperature differences between the source and the sink. In addition, itv is possible to recover the free energy of dry air by evaporation of water. The free energy can be defined as i (lo H1) 1 r where,

Rds the gas constant isthe heatof vaporization of water, and risthe relative humidity of air before vapor is added to it.

Further,since the vanes 26, of the rotor 22, are fixed relative to the rotor hub 24 and do not touch the rotor housing 12, no lubrication is required except for bearings. Also, considering the size of the apparatus, a large volume of air or gas can be handled. Another advantage is that apparatus constructed in accordance with this invention pan operate at low pressure differentials between the at- 10 mosphere and the gas within the sealed heat exchanger enclosure 50. i

Since certain changes may be made in the above described apparatus and diiferent embodimentsof the invention may be made without departing from the spirit and scope thereof, it is intended that all matter contained in the above description or shown in the accompanying drawings shall be interpreted as illustrative and notin a limiting sense.

I claim as my invention:

1. In a heat pump, the combination comprising, a rotor having a hub and a plurality of substantially equally spaced vanes fixed to said hub and extending radially out therefrom; a rotor housing having in consecutive order a closed first sector portion, an open second sector portion, a closed third sector portion, and an open fourth sector portion which is disposed to receive gas from ambient space and discharge gas to ambient space, said rotor housing being so disposed around said rotor as to be in close proximity to all of the peripheral edges of said plurality of vanes as they in operation rotate. into-said closed first-sector portion and into said closed third sector portion, to thus successively enclose incoming intervane compartments in said closed first sector portion and successively enclose outgoing intervane compartments in said closed third sector portion; a first port in said closed first sector portion of said rotor housing in successive communication with said incoming intervane compartments; a second port in said closed third sector'portion of said rotor housing in successive communication with said outgoing intervane compartments; an interconnecting member having a streamlined constriction in the midsection so formed to define a venturi pressure inverter passageway, one end of said interconnecting member being connected to said housing so as to be in communication with said first port and theother end of said interconnecting member being connected to said housing so as to be in communication with said second port, to thus effect .a rapid pulsating transfer of gas through said interconnecting member and between said incoming and said outgoing intervane compartments, to thereby effect the desired adiabatic compression and adiabatic expansion in said incoming and outgoing intervane compartments; means for preventing the direct passage of gas between adjacent incoming intervane compartments and between adjacent outgoing intervane compartments during that period when the vane, of said plurality of vanes, which separates said adjacent incoming intervane compartments'is in the position of said first port and during that period when the vane, of said plurality of vanes, which separates said ad- ,jacent outgoing intervane compartments is in the position of said second port; sealed heat exchanger enclosure means having heat exchangersurfaces and so enclosing said rotor housing at said open second sector portion that said enclosure can receive gas from said incoming intervane compartments so that said gas from said incoming intervane compartments impinges onsaid heat exchanger surfaces to effect av change in the vapor content of the gas and so that said changed gas is delivered to said outgoing intervane compartments; and means for effecting rotation of said vaned rotor.

2. In a heat pump, the combination comprising, a rotor having a hub and a plurality of substantially equally spaced vanes fixed to saidhub and extending radially out therefrom; a rotor housing having in consecutive order a closed first sector portion, an open second sector portion, a closed third sector portion and an open fourth sector portion, said rotor housing being so disposed around said rotor as to be in close proximity to all of the peripheral edges of said vanes as they in operation rotate into said closed first sector portion and into said closed third sector portion to thus successively enclose incoming intervane compartments in said closed first sector portion and successively enclose outgoing intervane compartments in said closed third sectofportion; a first port in said closed first sector portion of said rotor housing in successive communication with said incoming intervane compartments; a second port in said closed third sector portion of said rotor housing in successive communication with said outgoing intervane compartments; a sealed heat exchanger enclosure having heat exchanger surfaces and being so connected to said rotor housing at said open second sector portion that said enclosure can receive gas from said incoming intervane compartments so that said gas impinges on said heat exchanger surfaces to effect a change in the heat content of said gas and so that said changed gas is delivered to said outgoing intervane compartments; an ambient manifold open to ambient space and so connected to said rotor housing at said open fourth sector portion that said changed gas from said outgoing intervane compartments is discharged to said ambient space and a new charge of gas from said ambient space is delivered to said incoming intervane compartments; an interconnecting member having two ends and being so constructed as to define a venturi pressure inverter passageway, one of the ends of said interconnecting member being connected to said rotor housing so as to be in communication with said first port and the other end of said interconnecting member being connected to said rotor housing so as to be in communication with said second port, to thus effect a rapid transfer of gas through said interconnecting memher and between said incoming and said outgoing intervane compartments to thereby effect the desired adiabatic compression and expansion in said incoming and outgoing intervane compartments; a closing member on each of said vanes and carried thereby so as to prevent the direct passage of gas between adjacent incoming inter vane compartments and between adjacent outgoing intervane compartments during that period when the vane, of said plurality of vanes, which separates said adjacent incoming intervane compartments is in the position of said first port and during that period when the vane, of said plurality of vanes, which separates said adjacent outgoing intervane compartments is in the position of said second port; a blower in communication with said gas of said heat exchanger enclosure to modify the pressure of said gas in said heat exchanger enclosure; and means for effecting rotation of said vaned rotor.

3. In a heat pump, the combination comprising, a rotor having a hub and a plurality of substantially equally spaced vanes fixed to said hub and extending radially out therefrom; a rotor housing having in consecutive order a closed first sector portion, a second open sector portion, a third closed sector portion and an open fourth sector portion, said rotor housing being so disposed around said rotor as to be in close proximity to all of the peripheral edges of said vanes as they in operation rotate into said closed first sector portion and into said closed third sector portion to thus successively enclose incoming intervane compartments in said closed first sector portion and successively enclose outgoing intervane compartments in said closed third sector portion; a first port in said closed first sector portion of said rotor housing in successive communication with said incoming intervane compartments; a second port in said closed third sector portion of said rotor housing in successive communication with said outgoing intervane compartments; an interconnecting member so constructed as to define a venturi, having a central section, which functions as a pressure inverter, with the intake section of said interconnecting member connected to said rotor housing so as to be in communication with said second port and with said intake section converging eccentrically with respect to said second port into said central section and with the outgoing section of said interconnecting member highly streamlined and divergent and connected to said rotor housing so as to be in communication with said first port, to thus effect a rapid pulsating transfer of gas from said outgoing intervane compartments to said incoming intervane compartments with a minimum of flow of gas in the reverse direction through said interconnecting member, so that gas within said outgoing intervane compartments is adiabatically expanded and gas within said incoming intervane compartments is adiabatically compressed; a closing member on each of said vanes and carried thereby so as to prevent the direct passage of gas between adjacent incoming intervane compartments and between adjacent out oing intervane compartments during that period when the vane, of said plurality of vanes, which separates said adjacent incoming intervane compartments is in the position of said first port and during that period when the vane, of said plurality of vanes, which separates said adjacent outgoing intervane compartments is in the position of said second port; an ambient manifold, including a separate discharge portion and a separate intake portion having a precooler, open to ambient space and connected to said rotor housing at said open fourth sector portion so that cold gas from said outgoing intervane compartments is discharged through said discharge portion to said ambient space and a new charge of precooled gas is delivered to said incoming intervane compartments through said intake portion; a sealed heat exchanger enclosure having evaporating surfaces and being so connected to said rotor housing at said open second sector portion that said enclosure can receive said adiabatically compressed gas from said incoming intervane compartments so that said adiabatically compressed gas impinges on said evaporating surfaces; means for directing water onto said evaporating surfaces so that said adiabatically compressed gas that impinges on said evaporating surfaces is further cooled by evaporation of water; a blower for maintaining pressure within said sealed heat exchanger enclosure; and means for effecting a rotation of said vaned rotor.

4. In a heat pump, the combination comprising; a rotor having a hub and a plurality of substantially equally spaced vanes fixed to said hub and extending radially out therefrom; a rotor housing having in consecutive order a closed first sector portion, an open second sector portion, a closed third sector portion and an open fourth sector portion, said rotor housing being so disposed around said rotor as to be in close proximity to all of the peripheral edges of said vanes as they in operation rotate into said closed first sector portion and into said closed third sector portion, to thus successively enclose incoming and intervane compartments in said closed first sector portion and successively enclose outgoing intervane compartments in said closed third sector portion; a first port in said closed first sector portion of said rotor housing in successive communication with said incoming intervane compartments; a second port in said closed third sector portion of said rotor housing in successive communication with said outgoing intervane compartments; a sealed heat exchanger enclosure having evaporating surfaces and being so connected to said rotor housing at said open second sector portion that said enclosure can receive gas from said incoming intervane compartments so that said gas impinges on said evaporating surfaces; means for directing water onto said evaporating surfaces where rapid evaporation takes place thus cooling said water; a blower, functioning as a vacuum pump, connected to said enclosure for reducing the pressure of said gas within said enclosure below atmospheric pressure to speed evaporation of said water; an interconnecting member so constructed as to define a venturi, having a central section, which functions as a pressure inverter, with the intake section of said venturi connected to said rotor housing so as to be in communication with said first port and with said intake section converging eccentrically with respect to said first port into said central section and with the outgoing section of said venturi highly streamlined and divergent and connected to said rotor housing so as to be in communication with said second port, to thus effect a rapid pulsating transfer of gas from said incoming intervane compartments to said outgoing intervane compartments with a minimum of flow of gas in the reverse direction through said venturi, so that the gas within said incoming intervane compartments is adiabatically expanded and the gas within said outgoing intervane compartments is adiabatically compressed; a closing member on each of said vanes and carried thereby so as to prevent the direct passage of gas between adjacent incoming intervane compartments and between adjacent outgoing intervane compartments during that period when the vane, of said plurality of vanes, which separates said adjacent incoming intervane compartments is in the position of said first port and during that period when the vane, of said plurality of vanes, which separates said adjacent outgoing intervane compartments is in the position of said second port; an ambient manifold open to ambient space and so connected to said rotor housing at said open fourth sector portion that the gas heated by adiabatic compression from said outgoing intervane compartments is discharged to said ambient space and a new charge of vapor laden gas from said ambient space is delivered to said incoming intervane compartments; and means for effecting a rotation of said vaned rotor.

5. In a heat pump, the combination comprising, a rotor having a hub and a plurality of substantially equally spaced vanes fixed to said hub and extending radially out therefrom; a rotor housing having in consecutive order a closed first sector portion, an open second sector portion, a closed third sector portion and an open fourth sector portion, said rotor housing being so disposed around said rotor as to be in close proximity to all of the peripheral edges of said vanes as they in operation rotate into said closed first sector portion and into said closed third sector portion, to thus successively enclose incoming intervane compartments in said closed first sector portion and successively enclose outgoing intervane compartments in said closed third sector portion; a first port in said closed first sector portion of said rotor housing in successive communication with said incoming intervane compartments; a second port in said closed third sector portion of said rotor housing in successive communication with said outgoing intervane compartments; a sealed heat exchanger enclosure having cooling coils and being so connected to said rotor housing at said open second sector portion that said enclosure can receive gas from said incoming intervane compartments so that said gas impinges on said cooling coils to deliver heat thereto; means for supplying air under pressure to said sealed heat exchanger enclosure for the purpose of increasing the heat content of said gas by compression of said gas so that the temperature of said gas is elevated to well above the dew point of said gas so that no frost can form on said cooling coils; an interconnecting member so constructed as to define a venturi, having a central section, which functions as a pressure inverter with the intake section of said venturi connected to said rotor housing so as to be in communication with said second port and with said intake section converging eccentrically with respect to said second port into said central section and with the outgoing section of said venturi highly streamlined and divergent and connected to said rotor housing so as to be in communication with said first port, to thus effect a rapid pulsating transfer of gas from said outgoing intervane compartments to said incoming intervane compartments with a minimum of flow of gas in the reverse direction through said venturi so that gas within said outgoing intervane compartments is adiabatically expanded and gas within said incoming intervane compartments is adiabatically compressed; a closing member on each of said vanes and carried thereby so as to prevent the direct passage of gas between adjacent incoming intervane compartments and between adjacent outgoing intervane compartments during that period when the vane, of said plurality of vanes, which separates said adjacent incoming intervane compartments is in the position of said first port and during that period when the vane, of said plurality of vanes, which separates said adjacent outgoing intervane compartments is in the position of said second port; an ambient manifold open to ambient space and so connected to said rotor housing at said open fourth sector portion that chilled gas from said outgoing intervane compartments is discharged to said ambient space and a new charge of gas from said ambient space is delivered to said incoming intervane compartments; and means for effecting a rotation of said vaned rotor.

6. In a heat pump, the combination comprising, a rotor having a hub and a plurality of substantially equally spaced vanes fixed to said hub and extending radially out therefrom; a rotor housing having in consecutive order a closed first sector portion, an open second sector portion, a closed third sector portion and an open fourth sector portion, said rotor housing being so disposed around said rotor as to be in close proximity to all of the peripheral edges of said vanes as they in operation rotate into said closed first sector portion and into said closed third sector portion, to thus successively enclose incoming intervane compartments in said cfosed first sector portion and successively enclose outgoing intervane compartments in said closed third sector portion; a first port in said closed first sector portion of said rotor housing in successive communication with said incoming intervane compartments; a second port in said closed third sector portion of said rotor housing in successive communication with said outgoing intervane compartments; a sealed heat exchanger enclosure having cooling coils and being so connected to said rotor housing at said open second sector portion that said enclosure can receive gas from said incoming intervane compartments so that said gas impinges on said colling coils to thereby condense vapor from said gas; a duct leading from said enclosure to a blower; a power means for driving said blower to function as an evacuating pump; an interconnecting member so constructed as to define a venturi, having a central section, which functions as a pressure inverter with the intake section of said venturi connected to said rotor housing so as to be in communication with said first port and with said intake section converging eccentrically with respect to said first port into said central section and with the outgoing section of said venturi highly streamlined and divergent and connected to said rotor housing so as to be in communication with said second port, to thus effect a rapid pulsating transfer of gas from said incoming intervane compartments to said outgoing intervane compartments with a minimum of flow of gas in the reverse direction through said venturi.

so that the gas within said incoming intervane compartments is adiabatically expanded and the gas within said outgoing intervane compartments is adiabatically compressed; a closing member on each of said vanes and carried thereby so as to prevent the direct passage of gas between adjacent incoming intervane compartments and between adjacent outgoing intervane compartments during that period when the vane, of said plurality of vanes, which separates said adjacent incoming intervane compartments is in the position of said first port and during that period when the vane, of said plurality of vanes, which separates said adjacent outgoing intervane compartments is in the position of said second port; an ambient manifold open to ambient space and so connected to said rotor housing at said open fourth sector portion that the gas heated by adiabatic compression from said outgoing intervane compartments is discharged to said ambient space and a new charge of gas from said ambient space is delivered to said incoming intervane compartments; and means for effecting a rotation of said vaned rotor.

No references cited. 

1. IN A HEAT PUMP, THE COMBINATION COMPRISING, A ROTOR HAVING A HUB AND A PLURALITY OF SUBSTANTIALLY EQUALLY SPACED VANES FIXED TO SAID HUB AND EXTENDING RADIALLY OUT THEREFROM; A ROTOR HOUSING HAVING IN CONSECUTIVE ORDER A CLOSED FIRST SECTOR PORTION, AN OPEN SECOND SECTOR PORTION, A CLOSED THIRD SECTOR PORTION, AND AN OPEN FOURTH SECTOR PORTION WHICH IS DISPOSED TO RECEIVE GAS FROM AMBIENT SPACE AND DISCHARGE GAS TO AMBIENT SPACE, SAID ROTOR HOUSING BEING SO DISPOSED AROUND SAID ROTOR AS TO BE IN CLOSE PROXIMITY TO ALL OF THE PERIPHERAL EDGES OF SAID PLURALITY OF VANES AS THEY IN OPERATION ROTATE INTO SAID CLOSED FIRST SECTOR PORTION AND INTO SAID CLOSED THIRD SECTOR PORTION, TO THUS SUCCESSIVELY ENCLOSE INCOMING INTERVANE COMPARTMENTS IN SAID CLOSED FIRST SECTOR PORTION AND SUCCESSIVELY ENCLOSE OUTGOING INTERVANE COMPARTMENTS IN SAID CLOSED THIRD SECTOR PORTION; A FIRST PORT IN SAID CLOSED FIRST SECTOR PORTION OF SAID ROTOR HOUSING IN SUCCESSIVE COMMUNICATION WITH SAID INCOMING INTERVANE COMPARTMENTS; A SECOND PORT IN SAID CLOSED THIRD SECTOR PORTION OF SAID ROTOR HOUSING IN SUCCESSIVE COMMUNICATION WITH SAID OUTGOING INTERVANE COMPARTMENTS; AN INTERCONNECTING MEMBER HAVING A STREAMLINED CONSTRICTION IN THE MIDSECTION SO FORMED TO DEFINE A VENTURI PRESSURE INVERTER PASSAGEWAY, ONE END OF SAID INTERCONNECTING MEMBER BEING CONNECTED TO SAID HOUSING SO AS TO BE IN COMMUNICATION WITH SAID FIRST PORT AND THE OTHER END OF SAID INTERCONNECTING MEMBER BEING CONNECTED TO SAID HOUSING SO AS TO BE IN COMMUNICATION WITH SAID SECOND PORT, TO THUS EFFECT A RAPID PULSATING TRANSFER OF GAS THROUGH SAID INTERCONNECTING MEMBER AND BETWEEN SAID INCOMING AND SAID OUTGOING INTERVANE COMPARTMENTS, TO THEREBY EFFECT THE DESIRED ADIABATIC COMPRESSION AND ADIABATIC EXPANSION IN SAID INCOMING AND OUTGOING INTERVANE COMPARTMENTS; MEANS FOR PREVENTING THE DIRECT PASSAGE OF GAS BETWEEN ADJACENT INCOMING INTERVANE COMPARTMENTS AND BETWEEN ADJACENT OUTGOING INTERVANE COMPARTMENTS DURING THAT PERIOD WHEN THE VANE, OF SAID PLURALITY OF VANES, WHICH SEPARATES SAID ADJACENT INCOMING INTERVANE COMPARTMENTS IS IN THE POSITION OF SAID FIRST PORT AND DURING THAT PERIOD WHEN THE VANE, OF SAID PLURALITY OF VANES, WHICH SEPARATES SAID ADJACENT OUTGOING INTERVANE COMPARTMENTS IS IN THE POSITION OF SAID SECOND PORT; SEALED HEAT EXCHANGER ENCLOSURE MEANS HAVING HEAT EXCHANGER SURFACES AND SO ENCLOSING SAID ROTOR HOUSING AT SAID OPEN SECOND SECTOR PORTION THAT SAID ENCLOSURE CAN RECEIVE GAS FROM SAID INCOMING INTERVANE COMPARTMENTS SO THAT SAID GAS FROM SAID INCOMING INTERVANE COMPARTMENTS IMPINGES ON SAID HEAT EXCHANGER SURFACES TO EFFECT A CHANGE IN THE VAPOR CONTENT OF THE GAS AND SO THAT SAID CHANGED GAS IS DELIVERED TO SAID OUTGOING INTERVANE COMPARTMENTS; AND MEANS FOR EFFECTING ROTATION OF SAID VANED ROTOR. 